Drive for furnace charge distribution apparatus

ABSTRACT

A drive and mounting mechanism for a rotatable and angularly adjustable charge distribution device mounted in the throat of a blast furnace is disclosed. The drive mechanism includes a rotary disc mounted concentrically with the tubular feed spout through which charge material is delivered to the distribution device, the distribution device being suspended from the underside of the rotary disc, and a ring gear rotatably supported on the upper side of the disc and movable independently thereof. A drive shaft coupled to the ring gear passes through the rotary disc and is connected to means for selectively varying the inclination of the distribution device. The drive mechanism also includes means for rotating the disc and gear and for varying the speed ratio therebetween to thereby drive the inclination adjustment means drive shaft.

[ 1 June 4, 1974 1 DRIVE FOR FURNACE CHARGE DISTRIBUTION APPARATUS [75] Inventor: Edouard Legille, Luxembourg, Luxembourg [73] Assignee: S.A. Des Anciens Etablissements Paul Wurth, Luxembourg, Luxembourg [22] Filed: Apr. 30, 1973 [21] Appl. No.: 355,730

[30] Foreign Application Priority Data [-58] Field of Search 266/27; 214/17 CB, 18 V, 214/35 R, 35 A, 36, 37

[56] References Cited UNITED STATES PATENTS 1.668968 5/1928 Lambot 214/35 R 3,693,812 9/1972 Mahr et a1. 214/35 R Primary ExaminerGerald A. Dost [57] ABSTRACT A drive and mounting mechanism for a rotatable and angularly adjustable charge distribution device mounted in the throat of a blast furnace is disclosed. The drive mechanism includes a rotary disc mounted concentrically with the tubular feed spout through which charge material is delivered to the distribution device, the distribution device being suspended from the underside of the rotary disc, and a ring gear rotatably supported on the upper side of the disc and movable independently thereof. A drive shaft coupled to the ring gear passes through the rotary disc and is connected to means for selectively varying the inclination of the distribution device. The drive mechanism also includes means for rotating the disc and gear and for varying the speed ratio therebetween to thereby drive the inclination adjustment means drive shaft.

11 Claims, 6 Drawing Figures DRIVE FOR FURNACE CHARGE DISTRIBUTION APPARATUS BACKGROUND OF THE INVENTION:

1. Field of the Invention The present invention relates to the delivery of raw material to a furnace and particularly to a blast furnace. More specifically, this invention is directed to the drive and support mechanisms for an adjustable charge distribution device of the type intended for installation in the throat area of a shaft furnace. Accordingly, the general objects of the present invention are to provide novel and improved methods and apparatus of such character.

2. Description of the Prior Art As a result of increases in hearth cross-sectional area and throat pressure, control over the charging process of modern high output blast furnaces has come to be of critical importance. Prior art blast furnace charging apparatus, such as those characterized by the well known bell-type distributing devices and compensation chambers, do not permit adequate control over charge distribution in the case of large high pressure furnaces.

Considering further the widely known bell-type distributing devices for supplying raw material to the throat of a shaft furnace, it is well known that the use of such devices results in a charge distribution on the furnace hearth in accordance with a characteristic M- curve. Slight improvement in charge distribution can be achieved through the use of movable throat armor. Nevertheless, with the exception to be described below, the prior art has been unable to achieve uniform or controlled charge distribution. The inability to accurately control charge distribution, in turn, has resulted in non-uniform furnace gassing. Non-uniform furnace gassing prevents the furnace from operating at optimum efficiency and thus the prior art charge distribution devices have impeded the development of large high output blast furnaces and furnace processes.

The sealing of the throat of a blast furnace relative to the ambient atmosphere has presented a particularly serious problem to designers; this sealing problem being especially evident in the case of furnaces operated with a high counter-pressure at the throat. In the prior art the requisite sealing, which must accommodate the charging apparatus, could be achieved only through the use of very complex, costly and large devices. The necessity of employing costly sealing devices is, of course, contrary to the enhanced economy of operation and higher output inherent in the operation of a blast furnace with a high throat counter-pressure.

Apparatus which permits the random control of the charge distribution of a high pressure shaft furnace is disclosed in U.S. Pat. No. 3,693,8l2'which is assigned to the same assignee as the present invention. The apparatus of U.S. Pat. No. 3,693,812 permits elimination of the previously employed bell-type distribution devices and reduces throat sealing problems to a minimum. The apparatus of U.S. Pat. No. 3,693,8l2 accomplishes these vastly improved results in an uncomplicated and reliable manner.

The apparatus disclosed in U.S. Pat. No. 3,693,812 employs a rotary distribution chute and includes means for adjusting the pitch angle of the chute with respect to the central axis of the associated blast furnace; the

distribution chute being positioned in the furnace port or throat. Charge material, for example ore, is supplied to the distribution chute from a storage bunker, displaced vertically above the furnace throat, via a central collecting and supply spout. In accordance with the apparatus of U.S. Pat. No. 3,693,8l2 the distribution chute is mounted from the underside of a rotary ring which is concentric with the central supply spout. The rotary ring is connected to a main drive via a first rotary sleeve whereby the ring and thus the chute may be caused to rotate. Chute angular adjustment is achieved through the use of a second rotary sleeve having a camming slot therein; the second rotary sleeve being arranged externally of and concentrically with the first sleeve. The second rotary sleeve is driven synchronously with the first sleeve and means are provided for increasing or decreasing the speed of the second sleeve with respect to the first sleeve. For a further and detailed explanation of the construction and operation of the prior art rotary and angularly adjustable distribution chute reference may be had to U.S. Pat. No. 3,693,812. lt would appear to be sufficient herein to note that the pitch angle of the distribution chute of the apparatus of U.S. Pat. No. 3,693,812 is set by varying the position or relative speed of the two concentrically arranged rotary sleeves with any differencs in position or speed causing a cam follower coupled to the chute angular position actuator to travel along the camming slot in the second sleeve.

Although the drive and mounting mechanism of U.S. Pat. No. 3,693,812 constitutes a substantial step forward in the art, experience therewith has indicated that certain improvements were desirable. Thus, in the patented device the pitch angle adjustment of the distribution chute was limited by the highest and lowest points of the camming slot in the outer rotary sleeve. Also, in the patented device a number of components; for example the two rotary sleeves, the connecting means, the bearings and the drive means; are directly exposed to the furnace throat pressure and dust. Operation in such a harsh environment contributes to the stressing and wear of the distribution device components and particularly to the bearings.

It has also been determined that the substantial advantages provided by the distribution apparatus of U.S. Pat. No. 3,693,8 l 2 are somewhat offset by the difficulties encountered in dismantling and installing the apparatus. ln the patented device the mountings and bearings for the distribution chute are not accessible from the outside of the blast furnace with conventional disassembly devices and tools. Even with special tools it is very difficult to manipulate the chute from a working platform located on the outer wall of the furnace. Thus, the installation and dismantling of the patented distribution apparatus, as required for periodic-service, necessitates the shutdown of the furnace to thereby enable work inside the furnace throat. The necessity of working within the furnace, as is well known, exposes personnel to highly unfavorable working conditions.

SUMMARY OF THE lNVENTlON The present invention overcomes the above briefly discussed and other disadvantages by providing a novel and improved drive device for a rotary and angularly adjustable distribution chute of a shaft furnace charging installation. The present invention also encompasses a novel attachment and mounting device for connecting such a distribution chute to the drive in a manner which permits rapid and safe replacement of the chute.

Drive apparatus in accordance with the present invention comprises a rotary disc mounted concentrically with the material supply spout inside the furnace throat; the distribution chute being suspended from the underside of the rotary disc. A gear rotatable independently of the disc is mounted on the upper side thereof. This gear drives, via a shaft which passes through the disc, the means for angularly displacing the distribution chute whereby the inclination of the chute may be adjusted independently of the rotation thereof.

Also in accordance with the present invention the rotary and angularly adjustable distribution chute is supported at its material inflow end on one longitudinal side by a regulating arm which is actuated by the drive shaft; the shaft passing through the rotary disc and being coupled to the gear carried by but rotatable independently of the disc as noted above.

BRIEF DESCRIPTION OF THE DRAWING The present invention may be better understood and its numerous objects and advantages will become apparent to those skilled in the art by reference to the ac companying drawing wherein like reference numerals refer to like elements in the several figures and in which:

FIG. I is a perspective view of a preferred embodiment of a distribution chute drive in accordance with the present invention;

FIG. 2 is a cross-sectional side elevation view of th embodiment of FIG. I; 1

FIG. 3 is a cross-sectional, side elevation view depicting the drive mechanism of FIG. 1 coupled to a distribution chute installed in the throat of a shaft furnace;

FIG. 4 is a side view, partly in section, depicting the connecting device between a rotary and angularly adjustable distribution chute and the pitch angle adjusting portion of a drive in accordance with the present invention; I

FIG. 5 is an end view of the apparatus of FIG. 4; and

FIG. 6 depicts a pivot bearing mounting for the distribution chute; the mounting device of FIG. 6 being disposed on the opposite side of the chute with respect to the apparatus of FIGS. 4 and 5.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring first briefly to FIG. 3, a rotary and angularly adjustable distribution chute 64 is shown as mounted in the throat of a blast furnace. The drive means for controlling the movements of chute 64 in accordance-with a preferred embodiment of the invention may be seen by simultaneous reference to FIGS. 1 and 2. Rotational movement of the distribution chute is accomplished through use of a main drive motor 1 which is coupled to a main drive shaft 8 via a clutch 2, braking device 3 and drive gears 4 and 6. The main shaft 8 is provided with a pair of displaced gears or toothed wheels 10 and 12. The distribution chute is connected to a rotary disc 24 and the driving of disc 24 is accomplished from main drive shaft gear 12 via an intermediate gear means indicated generally at 11 and a rotary sleeve 22.'The intermediate gear means 11 includes a rotary cylinder 16 which engages, by means of a ring gear 14, gear 12 on main drive shaft 8. Rotary cylinder 16 supports a further ring gear 18 which engages a ring gear 20 arranged on the upper part of rotary sleeve 22. Accordingly, rotation of main drive shaft 8 will cause the rotary driving of sleeve 22 and thus also the rotation of disc 24 which is rigidly connected to sleeve 22. Restated, the rotary disc 24 and thus'the distribution chute is caused to rotate about the blast furnace axis A by energizing the main drive motor 1. The rotary disc 24 and its associated sleeve 22 are arranged concentrically with the central inlet pipe or feed spout 62 through which charge material is delivered to the distribution chute 64 of FIG. 3.

An auxiliary drive shaft 42 isdriven by gear 10 on main drive shaft 8 via a planetary gear system indicated generally at 13. The auxiliary drive shaft 42, in the manner to be described below, controls the pitch angle adjustment of the distribution chute independently of the rotation thereof. The planetary gear system 13 comprises a planet wheel 38, engaged by main drive shaft gear 10, a pair of intermediate gears 34 and 36 and an inner gear 32. The two intermediate gears 34 and 36, as may best be seen from FIG. 2, drive a second rotary disc 40 via respective drive shafts 35 and 37. The rotary disc 40 is rigidly connected to auxiliary drive shaft 42. The auxiliary drive shaft 42 passes through an opening provided therefore in ring gear 14 of the intermediate gear means l 1. Auxiliary drive shaft 42 is provided, at its lower end, with a further gear 44. Gear 44 in turn drives a ring gear 46 mounted on rotary disc 24;

gear 46 being coupled to rotary disc 24 and rotary sleeve 22 by means of ball or roller bearings 48 as best shown in FIG. 2 whereby ring gear 46 will rotate with but may also be caused to rotate independently of disc 24.

Ring gear 46 drives a pinion 50 mounted on a first end of a shaft 56 which passes through rotary disc 24; shaft 56 being rotatably mounted in disc 24 by means of bearings as shown in FIG. 2. Shaft 56 has, either formed or mounted thereon below disc 24, a worm gear thread 54. As may best be seen from F IG.- 1, the worm gear 54 drives a partial gear ring 58 via an intermediate gear 57. The shaft 60 of partial ring gear 58 is connected, in the manner to be described in the discussion of FIG. 3, to the distribution chute for the purpose of adjusting the pitch angle thereof.

The worm gear 54, intermediate gear 57 and partial ring gear 58 are isolated from the heat and flue dust in the furnace throat by means of a gear box 52 which is fixed to the underside of rotary disc 24; gear box 52 being depicted in FIGS. 1 and 3.

The inner gear 32 of the planet gear means 13 is driven by an auxiliary drive motor 25 via drive shaft 33, gears 30 and 28, a braking device 27 and a clutch 26.

Referring again to FIG. 1, and as described above, the main drive motor I imparts rotary motion to disc 24. With a properly selected transmission ratio through the various intermediate gears, drive motor 1 will also cause ring gear 46 to rotate at the same speed as disc 24; both disc 24 and gear 46 rotating about the axis A of the furnace. With no speed differential between disc 24 and gear 46, the shaft 56 of pinion 50 will remain in an unchanged position with respect to its axis of rotation; shaft 56 being carried along by rotary disc 24. Distribution chute 64 is, accordingly, caused to rotate about the furnace axis A without the angular position or inclination thereof relative to this axis being changed.

An increase or reduction of the speed of ring gear 46 relative to rotary disc 24 may be produced through the exercise of control over auxiliary motor 25; the output of motor 25 being applied to ring gear 46 via the planetary gear means 13 in the manner described above. A speed difference between ring gear 46 and rotary disc 24 results in pinion 50 being rotated whereby'worm gear 54 drives partial ring gear 58 to cause a change in the angle of inclination of the distribution chute relative to the blast furnace axis A. In one embodiment of the invention the rotary motor 25 was bidirectional whereby the motor could be reversed by means of changing the polarity of the energization signal applied thereto.

It is also possible, through judicious choice of the transmission ratio between the various gears of the drive system of the present invention, to achieve a synchronous rotational speed between disc 24 and ring gear 46 at a particular single speed of auxiliary motor 25 and an associated particular single speed of main drive motor Restated, synchronization of rotary disc 24 with ring gear 46 may be caused to occur at a particular ratio between the rotational speeds of the main drive motor 1 and the auxiliary motor 25. A variation in either direction of this speed ratio will cause a relative speed increase or decrease for ring gear 46 relative to disc 24 and, in the manner described above, this relative speed difference will produce a change in the angle of inclination of the distribution chute without the necessity of reversing auxiliary motor 25.

FIG. 3 depicts the installation of a randomly controllable charge distribution device in accordance with the present invention on a blast furnace. The charging installation is in the form of a superstructure on the blast furnace throat 66. The essential components of the installation, which is a bell-less charging apparatus, includes a pair of storage bunkers or intermediate charging hoppers 126, 126' which are provided with respective material discharge channels 128, 128'. Both of material discharge channels 128, 128 empty into the central inlet pipe or feed spout 62. The distribution chute 64 is arranged centrally in the blast furnace port or throat 66 and, in the manner described above, chute 64 is rotatable and may be adjusted in angle of inclination relative to the blast furnace axis A. The charging installation also includes the drive mechanism described above in the discussion of FIGS. 1 and 2 which imparts rotational and angular movement to chute 64. The two intermediate charging hoppers 126, 126' operate in accordance with a fixed cycle and are sealed relative to the outer atmosphere and/or furnace pressure by upper sealing valves, not shown, and lower sealing valves, 130, 130; the lower sealing valves being located at the lower ends of discharge channels 128, 128'. Discharge channels 128, 128 are provided with respective material retaining and flow control valves 132, 132' which regulate the rate of material flow from the intermediate charging hoppers 126, 126' into central feed spout 62.

The two intermediate charging hoppers I26, 126' may, if desired, be designed as weighing or quantity measuring hoppers so that the quantity of material in each hopper can be determined continuously during a charging operation and the flow control valves 132,

132' positioned in accordance with the measurement.

In the apparatus depicted in FIG. 3, charging hoppers 126, 126 are in fact weight measuring bunkers. As such, the hoppers 126, 126' must not be rigidly connected to the blast furnace. In the interest of obtaining an accurate measurement, angular displaceable corrugated support compensators 134, 136 and 134, 136', are provided for connecting the weighing hoppers to the blast furnace.

In operation, as soon as one of hoppers 126, 126' is filled with the requisite weight of charge material its upper sealing valve is closed. The charged hopper is subsequently pressurized to equalize the pressure in the hopper with that existing in the furnace throat. Accordingly, upon subsequent opening of the lower sealing valve, such as valves I30 and there will be no abrupt drop in furnace throat pressure which might disturb the blast furnace process. Charge equalization also facilitates opening of the lower sealing valve. When opened, the lower sealing valve is pivoted completely out of the path of flow of the material exiting the storage hopper and the sealing valve is consequently not exposed to wear and damage by the sliding charge material. With the lower sealing valve open the flow of material from the storage hopper into the central feed spout 62 and thence to distribution chute 64 is controlled by means of the appropriate one of flow control valves 132, 132.

During the charging process the distribution chute 64 will be caused to rotate and its pitch angle changed with respect to the blast furnace central axis A depending on the type of charging to be performed. Typically, chute 64 will describe a path during the charging operation which is dependent upon the quantity of material supplied to the furnace per unit of time; the movement of chute 64 typically being in accordance with a previously determined program to achieve the desired charge distribution.

As noted above, the distribution chute 64 is rotated by disc 24. As shown in FIG. 3, a chamber 68 is defined above disc 24 by the rotary disc itself. Rotary disc 24 does not seal chamber 68 relative to the blast furnace throat 66. Chamber 68 is, however, sealed relative to the ambient atmosphere by a pressure-tight jacket.'The drive described in the discussion of FIGS. 1 and 2 is partially located in a gear box 67 which is fixed to the upper outer wall of drive chamber 68. The rotary sleeve via which rotational motion is transmitted to disc 24 penetrates the partition between v gear box 67 and drive chamber 68 as clearly shown in FIG. 3. The auxiliary drive shaft 42, which serves to'bring about the pitch angle adjustment of the distribution chute, passes centrally through rotary sleeve 16 from gear box 67 to drive chamber 68. Sleeve 16 and shaft 42 are sealed, by means known in the art, to one another and sleeve 16 is in turn sealed in the partition between gear box 67 and chamber 68 whereby atmospheric pressure may be maintained in gear box 67 while drive chamber 68 is under substantially blast furnace throat pressure. By means of the concentric arrangement of shaft 42 relative to rotary sleeve 16, the sealing between these two members is exposed to wear only in the case of a relative angular speed difference between sleeve 16 and shaft 42. Restated, with shaft 42 and sleeve 16 synchronized in speed the sealing means therebetween is not effected by friction.

A particularly significant feature of the present invention is the ability to isolate the interior of gear box 67 from the interior of drive chamber 68 by conventional means. In the prior art the sealing of the pressure at the furnace throat relative to the ambient atmosphere, particularly in charging installations employing bells, has presented a problem which has defied adequate solution.

As will now be obvious, only those components of the drive mechanism which, because of sealing problems, can not be located in a cleaner environment are positioned within drive chamber 68. Thus, as may be seen from FIG. 3, drive chamber 68 includes, in addition to the rotary disc 24, gears 18 and 20, conical rotary sleeve 22, gears 44 and 46, and pinion 50.

In the interest of cooling and preventing contamination of the components within drive chamber 68, inert gas or purified and cooled blast furnace gas may be introduced into the chamber under an appropriately high pressure via connection 70. The pressure of the cooling gas delivered to chamber 68 ispreferably higher than the furnace throat pressure. As a result of this excess pressure, blast furnace flue dust is inhibited from penetrating from the blast furnace port 66 into chamber 68. As noted, the gas flow into chamber 68 also serves-to cool the drive portions which are exposed to the furnace throat temperature. To further protect the components in chamber 68 from the direct influence of the furnace throat temperature, the rotary disc 24 is provided with a heat resistant insulating layer on its underside.

The outer wall of drive chamber 68 is provided with a manhole or service port 72 via which the chamber becomes accessible should it become necessary to perform any repairs on the components of the drive system located in chamber 68.

The upper or material inflow end of distribution chute 64 is provided, on one of its longitudinal sides, with a support shaft rotatably mounted in a suspension device 74. As may be seen from a joint consideration of FIGS. 3 and 6, and as will be described in more detail below, the suspension device 74 is in the form of a jaw member detachably connected to rotary disc 24 by means accessible from the inside of drive chamber 68. The upper end of the opposite longitudinal side of the distribution chute is provided with a regulating arm 76 which may be seen from joint consideration of FIGS. 3 and 4. The chute 64 is firmly but detachably connected to arm-76. Regulating arm 76 includes or is connected to the transversely extending horizontal shaft 60 of FIGS. 1 and 3; shaft 60 being rotatable about its horizontal axis and accomplishing the pitch angle adjustment of distribution chute 64 in the manner previously described.

Referring now to FIGS. 4 and 5, the means by which rotation of shaft 60 is transmitted to the distribution chute 64 is shown in more detail. As noted, the shaft 60 and regulating arm 76 are preferably integral. As noted in the discussion of FIG. 1, a ring gear segment 58 on a first end of shaft 60 functions as a drive for the pitch angle adjustment; gear segment 58 typically being affixed to shaft 60 by a shrink fitting. Distribution chute 64 will be provided with a pair'of transversely outwardly extending shafts 82 and 84 having ends designed to effect the connection between the regulating arm 76 and chute 64. The ends of shafts 82 and 84 are provided with V shaped annular grooves. The regulating arm 76 is provided with groove seatings 86 and 88 thereby insuring that, upon insertion in the regulating arm 76, chute 64 is automatically centered. As may best be seen from FIG. 4, the regulating arm 76 is provided with a recess or cut-out which, when arm 76 is in the horizontal position, extends from groove seating 86 in a sloping manner to the upper edge of arm 76. The regulating arm 76 is also provided with a slot 126 which extends vertically from groove seating 88 to the upper edge of the arm. The grooved end of shaft 84 is inserted in groove seating 88 via slot 126. The groove seating 88 is arranged in-such a manner that shaft 84 can not move in the longitudinal direction of arm 76. The grooved end of shaft 82 is retained firmly in groove seating 86, and can not move in either the horizontal or vertical direction, by means of the cut-out 90 which is inclined relative to the regulating arm longitudinal axis. In the manner to be described below, the distribution chute 64 will be connected firmly to regulating arm 76 by means of locking the end of shaft 84 in its cooperating seating 88.

The introduction of shafts 82 and 84 of distribution chute 64 into their respective seatings 86 and 88 of regulating arm 76 is accomplished by first introducing shaft 82 through cut-out 90 into seating 86. Thereafter, by lowering chute 64, shaft 84 may be guided through slot 126 into seating 88. Finally, in the manner to be described below, shaft 84 is locked in seating 88.

The regulating arm 76 is also provided with an inclined bore 104. A key 92 will be inserted in bore 104. The underside of key 92 will contact an inclined truncated segment-shaped surface 106 on the end of shaft 84. Surface 106 on the end of shaft 84 is oriented parallelly with groove 104 and key 92 thus locks shaft 84 in seating 88. A bracket 102 formed from a thick metal sheet is attached, preferably by welding, to the jacket of chute 64. Bracket 102 is provided with an aperture which receives an end of key 92 as shown in FIG. 4; the key receiving portion of bracket 102 being approximately perpendicular to the axis of key 92 and bore 104. Key 92 is provided with an end plate 96 which is typically welded to the key. In order to insure that key 92 will beretained in bore 104 of the regulating arm 76, the end plate 96 on key 92 will be connected to bracket 102. The connection between bracket 102 and plate 92 will be by detachable means such as screw couplings inserted at 98 and 100.

The key 92 is preferably shaped, as shown in FIG. 4, in the interest of insuring that the key does not fall out of the aperture in bracket 102 upon intentional or accidental detachment of the screw couplings between plate 92 and bracket 102 at points 98 and 100. Thus, the upper portion 128 of key 92 is made thicker than the remaining portions thereof whereby the diameter of portion 128 is greater than the diameter of the aperture in bracket 102. Consequently, unintentional detachment of key 92 from bracket 102 is prevented by the end plate 96 and by the thickened portion 128 of the key. The end plate 96 is welded to key 92 after introduction of the end of the key through the aperture in bracket 102. The length of the reduced diameter portion of key 92 between plate 96 and portion 128 is such that the key can be removed satisfactorily and completely from bore 104 and slot 126 of regulating arm 76 before the enlarged portion 128 of key 92 contacts the bracket 102. I

As described above, distribution chute 64 is supported on one longitudinal side by means of regulating arm 76. The variation in the inclination of the distribution chute with respect to the blast furnace central axis is, as may best be seen from a joint consideration of FIGS. 1, 3 and 4, accomplished by transmitting the rotation of shaft 60 to regulating arm 76. As previously noted, the distribution chute 64 is held by the apparatus disclosed in H0. 6 on its longitudinal side disposed opposite to regulating arm 76.

Referring again to FIG. 6, it may be seen that the distribution chute 64 is provided, on the side opposite to that having shafts 82 and 84, with a further outwardly extending shaft 110; Shaft 110 is received in a bearing mounting 112 and locked therein by a clamping member or jaw 114. law 114 prevents the shaft 110 from falling out of mounting or block 112 but does not impede the rotation of shaft 110. Removal or repositioning of jaw 114 permits the rapid and easy disassembly of shaft 110 from the supporting mechanism.

Continuing with a discussion of FIG. 6, the bearing block 112 comprises an lower portion 116 and a upper portion 118 which are preferably formed as an integral unit. The lower portion 116 of the bearing block is solid while upper portion 118 is in the form of a yoke. The two lateral walls of the yoke portion 118 of bearing block 112 preferably have the same wall thickness and are welded to the underside of rotary disc 24. The width of the yoke groove is such that the jaw 114 can be passed therethrough with the jaw being slidable in the groove. Jaw 114 is retained, by means of a bolt 117, in the groove of yoke 118. By means of rotating jaw 114 about the bolt 117 the shaft 110 may be clamped in bearing block 112 or released for disassembly purposes as required.

The free end of the jaw 114; Le, the end displaced from the portion which contacts shaft 110; is attached to the head of a screw 108; the'means of attachment being a pin 124 which permits rotation of the end of the jaw member about an axis transverse to the axis of screw 108. The screw 108 passes through an opening 120 in rotary disc 24 and, on the upper side of disc 24, is held in place by means of a nut 122. The nut 122 is located in the drive chamber 68 and is therefore accessible via the port 72 (FIG. 3). .law 114 may be rotated about bolt 117 in a first direction by loosening nut 122 in the interest of disassembly of shaft 110 from bearing block 112. Conversely, tightening of nut 122 causes shaft 110 to be clamped in block 112.

The disassembly of a randomly controllable distribution chute in accordance with the present invention will now be briefly described. Referring to FIG. 3, it will be noted that the blast furnace wall is provided with an opening or port 78 which, during normal furnace operation, is sealed in a pressure tight manner. The furnace is also provided with a working platform 80 on the exterior wall adjacent to port 78. ln order to replace the distribution chute 64, after shutting down the furnace the port 78 is opened from the working platform 80. Chute 64 is rotated toward port 78 with the aid of the drive mechanism described above and is put into an approximately horizontal position. In this position the chute 64 partially projects through port 78. During normal operation the pitch angle of chute 64 is limited, for example by suitably positioned limit switches, so that it will not contact the inner wall of the furnace. During assembly and disassembly operations the limit switches will be rendered inoperative thereby permitting chute 64 to be brought into its horizontal position.

When in the horizontal position, chute 64 is affixed to a crane cross-bar which is, in turn, attached via a cable to a blast furnace crane. With the aid of the crane cross-bar the chute 64 can be assembled or disassembled without personnel entering the blast furnace port or throat. Thus, after chute 64 has been attached to the crane cross-bar, the port 72 on the outer wall of drive chamber 68 will be opened and the drive chamber entered by operating personnel. As noted above, the nut 122 and screw 108 are accessible from within chamber 68 and, accordingly, by means of loosening nut 122 jaw 114 is detached from its clamping position thereby rendering chute 64 ready for disassembly from the drive and support mechanism on the side opposite to the pitch angle regulating arm 76.

Simultaneously, chute 64 is released from regulating arm 76 from working platform 80. This is accomplished by detaching the coupling mechanisms between clamping key 92 and bracket 102 at points 98 and 100 of FIG. 4. The clamping key 92 is thereupon removed from slot 104. The distribution chute 64 is now ready for disassembly on the pitch angle drive side. Disassembly is achieved by moving chute 64 relative to regulating arm 76 so that shaft 84 is first removed from arm 76 and, by subsequently raising chute 64, shaft 82 is also removed from its seating; the lifting action of chute 64 to accomplish the unseating of shafts 82 and 84 being brought about by the previously mentioned crane crossbar. The distribution chute will now be sus pended freely on the crane cross-bar and may subsequently be brought into position for removal from the furnace throat. The assembly operation will, of course, take place in the reverse sequence to disassembly.

While a preferred embodiment has been shown and described, various modifications and substitutions may be made thereto without departing from the spirit and scope of the invention. Accordingly, it is to be understood that the present invention has been described by way of illustration and not limitation.

What is claimed is:

1. Drive means for a rotatable and simultaneously an-- output shaft means driven by said ring gear means, said output shaft means including an output shaft which passes through said disc and is rotatably mounted therein; 1

means for angularly displacing said movable member independently of the rotation thereof, said angular displacement providing means being coupled to said output shaft means; and

drive means for rotating said disc and ring gear means independently of one another.

2. The apparatus of claim I wherein said rotatable and angularly adjustable member is a material distribution device mounted within a shaft furnace and wherein said rotary disc and ring gear means are positioned about and concentric with tubular means for delivering material from the exterior of the furnace to said distribution device.

3. The apparatus of claim 2 wherein said drive means comprises: I

a main drive motor having a rotary output shaft;

means for coupling said main drive motor output shaft to said rotary disc; and

pitch angle adjustment drive means coupled to said ring gear means.

4. The apparatus of claim 3 wherein said pitch angle adjustment drive means comprises:

an auxiliary drive motor having a rotatable output shaft;

planetary gear means including a planet gear, an

inner gear and intermediate gear means;

means coupling said planetary gear means planet gear to said main drive motor output shaft;

means coupling said planetary gear means inner gear to said auxiliary drive motor output shaft; and

means coupling said planetary gear means intermediate gear means to said ring gear means whereby the speed ratio between said disc and ring gear means may be varied to thereby cause rotation of said output shaft means output shaft' 5. The apparatus of claim 3 wherein said means for coupling said main drive motor output shaft to said rotary disc includes:

a rotary sleeve concentric with the tubular material delivering means, said rotary sleeve being affixed adjacent one end thereof to said rotary disc;

a drive gear affixed to the exterior of said rotary sleeve at a point displaced from said rotary disc;

means coupling said main drive motor output shaft to said gear affixed to the exterior of said rotary sleeve.

6. The apparatus of claim 4. wherein said means for coupling said main drive motor output shaft to said rotary disc includes:

a rotary sleeve concentric with the tubular material delivering means, said rotary sleeve being affixed adjacent one end thereof to said rotary disc;

a drive gear affixed to the exterior of said rotary sleeve at a point displaced from said rotary disc;

means coupling said main drive motor output shaft to said gear affixed to the exterior of said rotary sleeve.

7. The apparatus of claim 6 further comprising:

bearing means supporting said ring gear means on said rotatable disc, said bearing means also coupling said ring gear means to said rotary sleeve. 8. The apparatus of claim 2 wherein said mounting means for said distribution device comprises: means rotatably supporting the distribution device at a first point adjacent a first end thereof; regulating arm means supporting said distributing device at said first end thereof in a region substantially oppositely disposed to said first point; and means coupling said regulating arm means to said output shaft means whereby rotation of said output shaft means will cause rotation of said regulating arm means about an axis transverse to the axis of said output shaft means.

' 9. The apparatus of claim 8 wherein said regulating arm means comprises:

a pair of displaced shafts extending from said distribution device; an elongated arm having recesses therein for receiving said shafts;

a rotatable axle extending transversely from said elongated arm, said transverse axle extension being rotatable and being connected to said coupling means.

10. The apparatus of claim 7 wherein said mounting means for said distribution device comprises:

means rotatably supporting the distribution device at a first point adjacent a first end thereof;

regulating arm means supporting said distributing device at said first endthereof in a region substantially oppositely disposed to said first point; and

means coupling said regulating arm means to said output shaft means whereby rotation of said output shaft means will cause rotation of said regulating arm means about an axis transverse to the axis of said output shaft means.

11. The apparatus of claim 10 wherein said regulating arm means comprises:

a pair of displaced shafts extending from said distribution device;

an elongated arm having recesses therein for receiving said shafts;

a rotatable axle extending transversely from said rotatable and being connected to said coupling means.

elongated arm, said transverse axle extension being 

1. Drive means for a rotatable and simultaneously angularly adjustable movable member comprising: a rotary disc; means mounting said movable member from the underside of said disc; ring gear means supported on the upper side of said disc for rotation therewith, said gear means being rotatable independently of the rotation of said disc; output shaft means driven by said ring gear means, said output shaft means including an output shaft which passes through said disc and is rotatably mounted therein; means for angularly displacing said movable member independently of the rotation thereof, said angular displacement providing means being coupled to said output shaft means; and drive means for rotating said disc and ring gear means independently of one another.
 2. The apparatus of claim 1 wherein said rotatable and angularly adjustable member is a material distribution device mounted within a shaft furnace and wherein said rotary disc and ring gear means are positioned about and concentric with tubular means for delivering material from the exterior of the furnace to said distribution device.
 3. The apparatus of claim 2 wherein said drive means comprises: a main drive motor having a rotary output shaft; means for coupling said main drive motor output shaft to said rotary disc; and pitch angle adjustment drive means coupled to said ring gear means.
 4. The apparatus of claim 3 wherein said pitch angle adjustment drive means comprises: an auxiliary drive motor having a rotatable output shaft; planetary gear means including a planet gear, an inner gear and intermediate gear means; means coupling said planetary gear means planet gear to said main drive motor output shaft; means coupling said planetary gear means inner gear to said auxiliary drive motor output shaft; and means coupling said planetary gear means intermediate gear means to said ring gear means whereby the speed ratio between said disc and ring gear means may be varied to thereby cause rotation of said output shaft means output shaft.
 5. The apparatus of claim 3 wherein said means for coupling said main drive motor output shaft to said rotary disc includes: a rotary sleeve concentric with the tubular material delivering means, said rotary sleeve being affixed adjacent one end thereof to said rotary disc; a drive gear affixed to the exterior of said rotary sleeve at a point displaced from said rotary disc; means coupling said main drive motor output shaft to said gear affixed to the exterior of said rotary sleeve.
 6. The apparatus of claim 4 wherein said means for coupling said main drive motor output shaft to said rotary disc includes: a rotary sleeve concentric with the tubular material delivering means, said rotary sleeve being affixed adjacent one end thereof to said rotary disc; a drive gear affixed to the exterior of said rotary sleeve at a point displaced from said rotary disc; means coupling said main drive motor output shaft to said gear affixed to the exterior of said rotary sleeve.
 7. The apparatus of claim 6 further comprising: bearing means supporting said ring gear means on said rotatable disc, said bearing means also coupling said ring gear means to said rotary sleeve.
 8. The apparatus of claim 2 wherein said mounting means for said distribution device comprises: means rotatably supporting the distribution device at a first point adjacent a first end thereof; regulating arm means supporting said distributing device at said first end thereof in a region substantially oppositely disposed to said first point; and means coupling said regulating arm means to said output shaft means whereby rotation of said output shaft means will cause rotation of said regulating arm means about an axis transverse to the axis of said output shaft means.
 9. The apparatus of claim 8 wherein said regulating arm means comprises: a pair of displaced shafts extending from said distribution device; an elongated arm having recesses therein for receiving said shafts; a rotatable axle extending transversely from said elongated arm, said transverse axle extension being rotatable and being connected to said coupling means.
 10. The apparatus of claim 7 wherein said mounting means for said distribution device comprises: means rotatably supporting the distribution device at a first point adjacent a first end thereof; regulating arm means supporting said distributing device at said first end thereof in a region substantially oppositely disposed to said first point; and means coupling said regulating arm means to said output shaft means whereby rotation of said output shaft means will cause rotation of said regulating arm means about an axis transverse to the axis of said output shaft means.
 11. The apparatus of claim 10 wherein said regulating arm means comprises: a pair of displaced shafts extending from said distribution device; an elongated arm having recesses therein for receiving said shafts; a rotatable axle extending transversely from said elongated arm, said transverse axle extension being rotatable and being connected to said coupling means. 